Thirty-two speed head



. Feb. 11, 1930. H. M. NoRRls Er AL THIRTY-TWO SPEED HEAD 2 Sheets-Sheet 1 Filed' Feb. 2Q. 1924 s l-Il H. M. NoRRls E'r AL THIRTY-Two SPEED HEAD Feb. Il, 1830.

2 sheets-sheet 2 Filed Feb. 20. 1924 lthrough the entire mechanism Patented Feb. 11, 1930 UNITED STATES PA'iiaiN'rv oFFieE HENRY M. NOR-RIS AND `DAVID C. KLAUSMEYER, OF CINCINNATI, OHIO, ASSIGNORS T0 THE CINCINNATI BICKFORD TOOL COMPANY, OF CINCINNATI, OHIO, A. CORPORA- TION 0F OHIO THmTY- Twosrnnn HEAD Application filed February 20, 1924. Serial No. 694,121.

end of which may be secured drills or taps of vvarious diameters. This drill spindle is usu- Lally rotated in either of two directions, from a shaft journaled lengthwise of the radial arm, which in turn derives its lmotion from a suitable motor or other prime-mover located in any convenient place such as, for example,

on the base at the foot of the column, on thev arm, or upon the top of the column.

Asis well understood by those skilled in theY art, the diameter of the drill or tap being used and the nature of the work being operated on'` determine the speed at which the sp indle should be rotated for maximum efficiency.

To effect the necessary variations in speed in the drill spindle there are usually provided which together give in the'neighborhood of twenty-four different spindle speeds from a single speed inthe prime mover. Of Vthese speed-change mechanisms the primary one usuallyis located adjacent the prime mover and provides the iner changes in ratio so that the motion which flows therefrom and will not be too abruptly changed. The secondary set (cornnionly termed the back-gears) is usually located in the drill head and provides the coai'ser changes in ratio,`inasmuch as comparatively few parts are a'ected bythe lastinentioned gear-changes. Thus to obtain a predetermined speed of rotation for a-certain drill it has been necessary for the operator first to manipulate certain gear-shift levers carried by the drill-headto effect the coarse speed adjustment and then to leave his position at his work and go to the opposite end of' themachine and (by shifting the gears of the primary speed-change mechanism) effect the finer or more accurate speed setting.

This location of the primary set of change ears remote from the position of the operab A tor,.when at his work, has rendered its frequent adjustmentso inconvenient that the tendency of the operator is to ignore the finer settings'obtainable only by the primary gear set and to rely on the nearest speed obtainable by adj ustnient of the back-gears, which necessaril;Y results in a sacrifice of efficiency.

ThisI invention` has for an object to provide in a radial drill a greater number of speed changes than is customarily provided, and

so to arrange. the gear sets and their controlling levers that the operator may conveniently and'accurately secure any available ,speed of rotation in the spindle without leaving his position at his work.

A further object of the invention is to prolvide in a drill-head a plurality of speed. changing gear-sets 'capable of producing a compara ively great number of speeds in the drill spindle and so to proportion the gear 'atios of the varioussets that the difference in ratio of the pairs of intermeshing gears of any gear set is inversely proportionate to. the

`mechanism adapted to be driven thereby. two independent speed-changing mechanisms in direction and speed may not be too abrupt) 'when the motion is reversed suddenly, as when the drill spindle is being used for tapping holes at a high rate of speed and when vthereupon the attendant throws the reversing lever to cause the tap quickly to be arrested before it gets too far into the hole and to cause it immediately to be reversed and rapidly withdrawn. y y

This invention also has for an object to combine with a Aspeed change mechanism as above referred to, a motion reversing mechanism and to provide an improved form of friction clutch therefor.

To provide an extremely slow speed in the spindle it is necessary that the spindle be finally actiiatedby a gear of large diameter which is driven by a relatively small. pinion.v

This large gear, if fixed to the spindle, acts during rapid rotation as a species of fly-wheel and thereby causes undue strain on the friction drive when the motion is reversed. Like- 'is to provide a disconnectible connection,.in

the form of an improved clutch, between the large gear and the spindle, whereby the large gear may be maintained permanently in mesh with its driving pinionand operatively connected with the spindle only when an extremely slow speed is required, whereby the fy wheel effect of the large gear and the clashing of fastand slow running teeth is precluded.

These and other objects are attained by` combining in the drill-head three independent speed change mechanisms namely primary, secondary and tertiary gear-sets. Of these the primary set is designed to receive power at a single speed from the horizontal shaft journaled in the radial arm and transmit it to the secondary set in any one of four different speeds. As the primary set must necessarilyfactuate considerable mechanism the difference in ratio between the pairs of driving and driven gears is. relativelv small; the ratios being approximately 1 to .9, 1 to 1, 1 to 1.12 and 1 to 1.25, the same being in geometrical progression of the value 1.12.

The secondary gear-set provides two speeds which doubles thefour speeds received from the primaryset. As the mechanism actuated by this gear set is somewhat less than that actuated by the primary set the diierence in Iratio between the pairs of driving and driven gears thereof may be proportionately greater or in the neighborhood of 1 to .643 and-1 to 1.

The primary and secondary gear sets provide the finer speed controls and correspondin their actionto the primary set (or speedbox control) of the usual commercial form of radial drill. v.

The eight speeds from the secondary .gear set is delivered to a tertiary gear set operatively connected with the drill spindle and which provides four speed changes, or in other words which multiplies the eight speeds received from the secondary set into thirtytwo speeds in the spindle. This tertiarygear set corresponds to the usual back-gears and as' they actuate only the spindle, the difference in ratio between the various pairs of gears thereof may be comparatively greater,

than in the primary and secondary sets. The ratios of the driving and driven gears of the tertiary set may be substantially as 1 to .094; 1 to .226; 1 to .548; and 1 to 1.32, the same being in geometrical progression by the multiplier 2.4.

The above described three'gear sets a'ord thirty-two speeds from a single s peed inthe prime mover and varying 1n ratio from approximately 1 to :05 to 1 to 1.65. The first to produce one extreme .throughout the three gear sets. This may mentioned ratio may be attained by so connecting the gears of the three gear sets as (the slowest) be eifected by meshing together the gears A 'and A of gear set X; gears F and F of gear set Y; and gears G and G-I and [-J and J of gear set Z, the ratios of which are, respectively 1 to .9-1 to .643-1 to .5118-132 to 1-1 to .226 thus giving throughout the three gear sets a ratio of approximately 1 to .05. Likewise by meshing the gears D and D of the gear set X; gears E and E of gear set Y and by effecting a drive from shaft 0 to the spindle drive-sleeve through clutch H-H, gears l and I and clutch K, the other extreme ratio (the fastest) will be effected, to wit 1 to 1.65. This ratio is the result of the ratios between the gears D and D-E and E-I and I-which are respectively 1.25 to 1; 1 to 1 and 1.32 to 1. The intermediate ratios are obtained by other settings of the gear units and clutch elements as illustrated in Fig. 6 and hereinafter described.

From the foregoing it will be observed that the nearer the approach to the final delivery of the power the coarser may be the speed adjustments.

The means for reversing the direction of rotation of the spindle and the details of construction of the improved clutchwill be described later.

Other objects and advantages will be in part indicated in the following description and in part rendered apparent therefrom in connection with the annexed drawings.

To enable others skilled in the art so fully to apprehend the underlying features hereof that they may embody the same in the various'ways contemplated by this invention, drawings depicting a preferred typical construction have been annexed as a part of ,this disclosure and, in such drawings, like characters of reference denote corresponding parts throughout all the views, of which:-

Fig. 1 is a sectional development showing the improved speed-regulating mechanism connecting the horizontal drive shaft of radial drill arm with the spindle of a radial drill (all of this mechanism being carried in the drill-head). Fig. 2 is a section taken transverse to Fig. l showing the means for reversing the direction of rotation of the spindle. Fig. 3 is a modification somewhat similar to a portion of Fig. 1 but showing the means for disconnectibly connecting the large slow-speed gear with the spindle. Fig

4 is a section on the line 4 4 of Fig. 2, showingl the clutch actuating means. Fig. 5 is a detail section showing more clearly the means for expanding the friction clutch ring, and Fig. 6 is a diagrammatic View illustrating` the relation and action of the various in the shaft a.

a primary gear-set X comprising gear members A-A, B-B, C-C and D-D provides means for transmitting to a shaft b any one of four speeds, from a single speed A second gear set Y comprising gears E--E and -F-F double the f shaft d,

four speed transmitted thereto and produce eight speeds in a shaft c. A third -speed regulating mechanism Z connects the shaft c with the drill spindle e and multiplies the eight speeds of that shaft into thirty-two speeds in the spindle. The four trains of mechanism for so multiplying the number of speeds comprise 1st :-gears G-G, I-I, and gears J and J 2nd :-gears G-G and I-K; 3rd z-clutch H--H. shaft d and gears J -J and 4th :clutch H-H,

'--I and K.- Thus it is seen thatby means of'three independent speed changing mechanisms, all of which are carried in the drill head, the single speed in the shafts P and a are multiplied into thirty-two speeds in the spindle e.

Turning now to Figs. 1 and 2, power is introduccd-into the drill-head by means of the shaft P to which is keyed a sleeve 1. Upon this sleeve are loosely journaled bevel gears 2 and 3 which are maintained permanently in mesh with a bevel gear 4 fixed upon a shaft a. Suitable clutch-mechanisms 5 and 6 are provided for selectively securing either of the gears 2 and 3 to the sleeve 1, dependent upon the direction of rotation desired in the spindle.

' Within the drill head, and parallel with the shaft a, are journaled shafts b, c and d, and the usual drill spindle e. For convenience of location the shafts c and d may be arranged coaxially as shown in Fig. 1. Upon the shaft a are splined two gear members and 8 providing respectively, spur-gears A and B, and C and D. These gears are adapted selectively to be meshed with gears D provided by non-translatable gear members 9 and 10 splined to the shaft b. The gears A, B, C, D and A', B', C

, and D constitute the gear set X previously referred to (see Fig. 6)

The gear-member 9 also provides a gear E which at certain times, meshes with a like gear E forming a part of a shiftable gear member 11 splined to the shaft 0. The driven gear B also acts as a driver F adapted to mesh with a gear F provided by the shiftable gearmember 11. The gears E, E and F, F

comprise the gear set Y'Which doubles the four speeds available in the shaft b.

Upon the shaft c is also splined a shiftable gear member 12 formed with a gear Gry and a clutch-element H. The clutch-element H is adapted to be brought into mesh with a clutch-element H formed in a member Hc fixed upon a shaft d, journaled in the drillhead coaxial with the shaft c. The shaft d carries a pinion J which is adapted to transinit slow rotary motion to the spindle e through its connection with a large gear J provided by a shiftable gear-unit 13 splined tothe spindle. Slow motion may also be transmitted to the spindle from the gear member 12 by meshing the gear G thereof with the gear G forming a part of a gearunit 15 loosely journaled on a bushing 16 surrounding the spindle. Tith the gears G and G in mesh power flows through gears I and I to the member H* secured to the shaft d and thence through pinion J and gear J to the spindle. The clutch 'unit 13 also provides a clutch K which may be brought into mesh with gear I, and thus receive motion from the member 12 either through members H, H,I and I or G, Gr' and I. The means above described for connecting the shaft c with the spindle e comprises the tertiary gear set Z which provides the coarser speed adjustments. Fig. 3 shows a modified construction for operatively connecting the gear I with the large gear J and for connecting the gear J with the spindle. This modification consists in loosely journaling the gear J on a sleeve s splined` to the spindle e and maintaining it permanently in mesh with the pinion J. A shiftable clutch member 17 splined to the sleeve s is provided at its opposite ends with clutcheleinents 18 and 19 adapted respectively to connect. with the spindle sleeve either the gear I or a clutch 2O carried by the hub of the gear J This construction is preferably for some purposes as it permits the large gear to be disconnected lfrom the spindle during rapid rotation of the spindle whereby the gear J is prevented from acting as a flywheel. Furthermore this construction precludes shifting of the gear into and' out of mesh with the pinion J and thereby the clashing of fast and slow running gears is obviated.

It is to be understood that the members 7 8, 11, 12, 13 and 17 are adapted to be shifted by means of suitable hand-levers carried by the drill-head, but as the specific construction of these devices form no part of the present invention, illustration thereof is deemed unnecessary.

As'before stated, the bevel gears 2 and 3 engagement, each of the gears is formed with cured thereto) loosely journaled upon the sleeve 1 and formed" with a chamber 22. Fixed to the sleeve l, as by means of keys 23, which also serve to secure the sleeve to the shaft P) .are collars 24 which extend within the chambers 22 and support friction clutchrings 25. These clutch-rings are split, as shown at t in Fig. 5, and have one end seated against an abutment or stop-pin 26 secured in the collar 24. The opposite ends of the rings are engaged by cam-surfaces 27 formed in short rock-shafts 28, which when rocked in one direction act to expand the friction clutch-rings 25 and cause them to lock the hubs 21 of the gears 2 and 3 to the drive collars 24. The rock-shafts 28 are preferably actuated by means of rock-arms 29 secured thereto which, in turn, are moved by means of a manually shiftable slide bar 30 fitted within a recess 31 in the sleeve 1. This slidebar is provided with bevelled ends 32 which engage. the rounded ends of contact screws carried by the rock-arins 29.

These contact screws are adjustably secured in the rock-arms 29 and are maintained in their adjusted positions by the cramping action of locking plates 36 through which the screws are threaded. Screws 37 passing through the plates 36 and threaded into the arms 29, serve to depress one end of the plates to produce the necessary crampingr action.

Slidably mounted on the sleeve 1 and fixed to the slide-bar 30 as by means of screws 34 is a grooved clutch actuating collar 35adapted to be shifted (by means of a suitable handlever, not shown) either to the left or right from the position shown in Fig. 2 to connect either the gear 2 'or the gear 3 with the power shaft.

Inasmucli as the friction clutches are actu- I ated directly from the single-speed shaft and y all of the speed changing mechanism is located between the clutches and the drill spindles the clutches have a constant working condition which permits them to be adjusted to a'nicety which is precluded in other constructions wherein the clutches are operated at varying speeds.

Without further analysis, the foregoing will so fully reveal the gist of this invention that others can, by applying current knowledge, readily adapt it for various utilizations by retaining one or more of the features that,

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from the standpoint of the prior art, fairly constitute essential characteristics of either the generic or specific aspects of this invention and, therefore, such adaptations should be, and are intended to be, coinprehended within the meaning and range of equivalency of the following claims Having thus revealed this invention, we claim as new and desire tosecure the following combinations and elements, or equivalents thereof, by Letters Patent of the United States: v

1. A speed control mechanism for drill heads combining a power shaft; a spindle; three serially arranged speed change devices carried by said drill head and operatively connecting said shaft and spindle, each of said devices comprising a plurality of shiftable and non-sliiftable gears of varyiner ratio, the difference in ratio between the driving and driven gears of the first set being in goinetrical progression of ap roximately ,1.12, and the difference in ratio etween the driving and driven gears of the last gear-set beingin geometrical progression of approximately 2.4, whereby the difference in ratio of the driving and driven gears throughout the transmission is inversely proportionate tothe amount of mechanism actuated thereby.

2. A speed controlling mechanism combining a power shaft P; a second shaft a; means for rotating the second shaft from said power shaft; a third shaft Z) parallel with said lsecond shaft; a four-speed change gear mechanism comprising two gear units, each providing two driving gears, splined to said second shaft and four driven gears rotatably journaled coaxial with said third shaft, said driving and driven gears being adapted selectively to be engaged; a fourth shaft c parallel with the third shaft; a two-speed change gear mechanism connecting said third and fourth shafts and comprising two driving gears on said third shaft, one of which is one of the driven gears of the first named speed change mechanism, andl two driven gears splined to said fourth shaft said driving and driven gears being adapted selectively to be engaged; a fifth shaft al arranged with its axis in alignment with the axis of said fourth shaft; a power delivery element (16) a fourspeed change gear mechanism connecting said fourth shaft with said power delivery element and comprising a combined gear and clutch elementA splined to the fourth shaft c; a combined gear and clutch element secured to the fifth shaft d, said clutch elements being adapted to be engaged; a gear unit (15) loosely journaled on said power delivery elementand providing gears G and I adapted to be engaged with the gears of the combined gear and clutch elements; a gear J fixed to connected with said ing and driven gears of varying diameters, between which pairs the difference in ratio is comparatively'slight and varies in geometrical progression of approximately 1.12; a secondary speed change mechanism between said, third and fourth shafts comprising two pairs of driving and driven gears, between which the difference in ratio is as great as the extreme difference between the gears of said primary speed change mechanism, a tertiary speed change mechanism between said fourth shaft and said spindle comprising pairs of driving and driven gears, between which the difference in ratio varies in geometrical progression of which the multiplier is approximately twice that in the primary speed change mechanism, said three speed change mechanisms combining to give to said spindle thirty-two speeds from -a single speed in the power shaft and varying in ratio from approximately 1 to .O5 to 1 to 1.65. 4. A speed regulating mechanism for drill spindles combining a power shaft; second, third and fourth shafts journaled in the drill head and arranged lin parallelism; means for rotating said fourth shaft at varying speeds from said power shaft; a spindle; a sleeve operatively connected with said spindle; a fifth shaft arranged co-axially with said f fourth shaft a high speed drive between said fourth shaft and said spindle including a gear member splined to said fourth shaft; a gear member journaled on said sleeve; and means for establishing a driving connection between said gear members; a low speed drive between said fourth shaft and said spindle including a pinion on said fifth shaft and a large gear journaled on said sleeve and meshing with said pinion; means for driving said fifth shaft from said fourth shaft; and a shiftable clutch member for selectively establishing adriving connection between either said high or low speed drive and said sleeve. 5. A back-gear mechanism for drilling machines combining a first shaft 0 and a second shaft d arranged upon a common axis; a spindle-driving sleeve; two spindle-driving units supported coaxil with said sleeve andv providing three gears J, I, G; a gear splined to said first shaft c; two gears J and I' fixed to the second shaft d a first clutch mechanism between the gear on the. first shaft and one of the gears on the second shaft; a second clutch mechanism between two of the gears on the spindle-driving sleeve, one element of the last named clutch mechanism being permanently connected with said spindle-drivin sleeve, said gears and clutch mechanism being relatively shiftable to afford four drives from said first shaft c to said spindle sleeve as follows: first, through gears G', I--I, J-J and the second clutch mechanism; second, through the first clutch mechanism, gears J--J and the second clutch mechanism; third, through gears G--G and the second clutch mechanism; fourth, through the first clutch mechanism, gears I-I and the second clutch mechanism.

6. A speed change mechanism combining a first shaft c; a second shaft d, said shafts being arrangedupon a common axis; a member to be rotated; clutch mechanism adapted to effect a driving connection between said two shafts; a gear splined upon the rst shaft; two gears fixed to the second shaft; three gears rotatably journaled coaxial with the member to be rotated, one of the last named gears being complemental to the gear on the first shaft c and the others being complemental to the two gears on the second shaft d, a clutch mechanism for securing said three gears to said member, certain ones of said gears and said clutch mechanisms be.

ing shiftable to effect four drives from said shaft c to said member, substantially as described.

7. A back-gear mechanism for drilling machines comprising a driving shaft 0; a driven shaft d a spindle; a combined gear and clutchl element splined to the driving shaft; a combined gear and clutch element secured to said driven shaft said clutch elements being adaptedv to be engaged; a gear-unit loosely journaled coaxial with said spindle and providing gears Gr and I adapted to be engaged by the 'gears of said combined gear and clutch elements; a gear J fixed to said driven shaft; a gear coaxial with the spindle and adapted to be driven by said gear J and means selectively to cause either said gear J or said gear I to rotate said spindle.

In witness whereof, we have hereunto subscribed our names.

HENRY M. NORRIS. DAVID C. KLAUSMEYER. 

